EP1811151B1 - Moteur à combustion à piston élévateur - Google Patents

Moteur à combustion à piston élévateur Download PDF

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Publication number
EP1811151B1
EP1811151B1 EP06025534A EP06025534A EP1811151B1 EP 1811151 B1 EP1811151 B1 EP 1811151B1 EP 06025534 A EP06025534 A EP 06025534A EP 06025534 A EP06025534 A EP 06025534A EP 1811151 B1 EP1811151 B1 EP 1811151B1
Authority
EP
European Patent Office
Prior art keywords
lever
guide
transmission lever
internal combustion
piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP06025534A
Other languages
German (de)
English (en)
Other versions
EP1811151A3 (fr
EP1811151A2 (fr
Inventor
Markus Meyer
Frank Van Der Seylberg
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
IAV GmbH Ingenieurgesellschaft Auto und Verkehr
Original Assignee
IAV GmbH Ingenieurgesellschaft Auto und Verkehr
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by IAV GmbH Ingenieurgesellschaft Auto und Verkehr filed Critical IAV GmbH Ingenieurgesellschaft Auto und Verkehr
Publication of EP1811151A2 publication Critical patent/EP1811151A2/fr
Publication of EP1811151A3 publication Critical patent/EP1811151A3/fr
Application granted granted Critical
Publication of EP1811151B1 publication Critical patent/EP1811151B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F02B75/048—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable crank stroke length
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines

Definitions

  • the invention relates to reciprocating internal combustion engines with a crank mechanism and an indirectly coupled to the piston, the cylinder axis intersecting transmission lever, which is hinged on the one hand to a connecting rod of a crank mechanism and on the other hand guided in a cylinder block, but adjustable storage.
  • a crank mechanism with a connecting rod is coupled via its outer connecting rod eye to one end of a transmission lever which intersects the cylinder axis and whose other end is mounted on an eccentric of a cylinder block pivotally mounted control shaft.
  • a second, connected to the piston guided in the piston connecting rod is articulated.
  • By rotating the adjusting shaft mounted in the cylinder block with the eccentric displacement of the transmission lever takes place transversely to the cylinder axis.
  • the effective lever arm ratios of the two hinged connecting rods change based on the pivot point of the transmission lever on the eccentric of the control shaft little and also the size of the stroke.
  • the invention has for its object to achieve a greater variation in the translation of movements between the crank mechanism and piston in a generic internal combustion engine.
  • the pull and push rod connected to a piston of the internal combustion engine at its end facing the transmission lever on a guide, which is preferably designed as a pivotally mounted shoe, which engages in a longitudinally extending on the transmission lever guide.
  • the transmission lever is pivotally connected on the one hand with a connecting rod of the crankshaft and on the other hand, the transmission lever with an actuator, for variably adjusting the articulation of the pull and push rod to the transmission lever connected.
  • the guide of the pull and push rod is effected by a guide lever which is pivotally connected on the one hand with the pull and push rod and on the other hand is pivotally articulated on the cylinder block.
  • the shoe can alternatively as any guide which displaceably guides the connecting rod on the transmission lever, z. B. as a slot in the transmission lever, in which engages a pin formed on the connecting rod, be formed.
  • crank mechanism and piston With the embodiment according to the invention, a greater variation of the translation of movements between crank mechanism and piston can be realized than in the previously known generic solution. It move in addition to the piston in the first embodiment, only three transmission elements oscillating and that is the transmission lever, a connecting rod and the piston connected to the shoe and provided with pull and push rod.
  • the necessary guidance of the pull and push rod of the piston also takes place by a guide lever, which is mounted to reduce the forces occurring vertically displaceable on the cylinder block.
  • Another variant provides to guide the pull and push rod of the piston in place of the guide lever by a parallel to the cylinder axis arranged slide.
  • FIG. 1 shows the engine of a reciprocating internal combustion engine according to the invention in a schematic representation.
  • a cylinder 1 is arranged, in which a piston 2 moves and forms a volume-variable working space in a known manner depending on the size of the stroke.
  • the crankshaft 3 runs in a bearing 30ZB in the cylinder block, which is arranged offset to the cylinder axis ZA, in the direction of rotation DR.
  • a connecting rod 4 is mounted, whose outer bearing eye is hinged at the end of a transmission lever 5.
  • the piston 2 is positively connected to a pull and push rod 6, at the other end a pin 61 is arranged, which engages in a slot 51 of the transmission lever 5.
  • the transmission lever 5 is pivotally mounted in an adjustable manner guided in the cylinder block bearing 8.
  • a form-fitting bearing guide 8ZB is arranged, in which the bearing 8 can be set determined by an actuator, not shown in position.
  • the controllable by the actuator, not shown changes in the position of the bearing 8 are in FIG. 1 represented symbolically by the arrow designated S8.
  • the bearing guide 8ZB is always directed transversely to the cylinder axis ZA, but it can be arranged at right angles or in an expedient manner extending inclined. Inclined to the cylinder axis ZA extending bearing guides 8ZB are not shown in the figures.
  • a guide lever 9 is pivotally articulated, which is hinged on its side remote from the pull and push rod 6 side pivotally mounted on the cylinder block ZB.
  • the sliding connection between the pull and push rod 6 and the transmission lever 5 can also, as in FIG. 8 represented by means of a pivotally hinged at the lower end of the pull and push rod 6 slide shoe 7, which engages positively in a extending in the longitudinal axis of the transmission lever 5 guide 50.
  • FIG. 2 is the engine accordingly FIG. 1 , but shown in a setting for large stroke of the piston 2.
  • the bearing 8 of the transmission lever 5 is displaced to the left along its bearing guide 8ZB in the cylinder block. During a revolution of the crankshaft 3, this results in a larger stroke movement of the piston 2 than in FIG. 1 shown.
  • FIG. 3 shows the engine in a setting according to FIG. 2 for large stroke, but with a position of the crankshaft 3, in which the piston 2 has reached the bottom dead center UT.
  • the pull and push rod 6 pivots from its vertical and is forcibly guided by the guide lever 9 in the slot 51 of the transmission lever 5.
  • FIGS. 4 to 7 show a variant of the solution according to the invention, in which the friction between the shoe 7 and the pin 61 of the pull and push rod 6 and the transmission lever 5 is further reduced.
  • the adjustment of the stroke of the piston 2 is also effected by moving the transmission lever 5 by an adjusting drive, so that the articulation point of the pull and push rod 6 is moved to the transmission lever 5 according to the stroke to be set.
  • the leadership of the pull and push rod 6 is also carried out by the guide lever 9, but pivotally mounted on a cylinder block ZB, vertically displaceable sliding guide 10 is articulated.
  • the actuator for setting and changing the stroke consists essentially of a controllably driven worm shaft 12, which is in operative connection with a worm wheel 11.
  • a controllably driven worm shaft 12 which is in operative connection with a worm wheel 11.
  • the worm wheel 11 is pivoted about its pivot point 16.
  • the worm wheel 11 is pivoted either up or down.
  • the worm wheel 11 is spaced from the pivot point 16 on the one hand via a pivotally hinged feed lever 14 with the guide lever 9 and a sliding guide 10 hingedly connected.
  • the worm wheel 11 is pivotally connected via a pivotally hinged rocker arm 15 with the transmission lever 5.
  • the pivotable articulation of the feed lever 14 and the rocker 15 on the worm wheel 11 takes place via a common pivot pin. Also via a common pivot pin, the articulation of the feed lever 14 and the guide lever 9 to the arranged on the cylinder block ZB, vertically displaceable sliding guide 10.
  • a two-lever 13 is pivotally hinged, the other end is stationary, but pivotally mounted on the cylinder block ZB.
  • the pivotal movement of the rocker arm 15 about the pivot point 17 of the transmission lever 5 is moved, wherein the articulation point of the pull and push rod 6 on the transmission lever 5 according to the is shifted to be set stroke.
  • the pivoting of the worm wheel 11 displaces the guide lever 9 articulated on the sliding guide 10, which also influences the adjustment of the articulation of the pull and push rod 6 on the transmission lever 5.
  • FIGS. 4 and 6 in each case a large stroke adjustment is shown, wherein FIG. 4 the position of the piston 2 in the bottom dead center UT and FIG. 6 the position of the piston 2 at top dead center TDC shows. From the illustrations it can be seen that the sliding guide 10 is in its lower position and the articulation point of the rocker 15 and the feed lever 14 is located on the worm wheel 11 close to the worm shaft 12.
  • FIG. 5 shows the piston 2 at bottom dead center UT while in FIG. 7 the position of the piston 2 is shown at top dead center OT.
  • FIGS. 8 to 10 Another variant of the solution according to the invention is in the FIGS. 8 to 10 shown.
  • the leadership of the pull and push rod 6 does not take place by means of the guide lever 9, but by a cylinder block ZB arranged slide 60ZB.
  • the transmission lever 5 is also slidably and pivotally mounted to adjust the stroke in a displaceable by an actuator not shown bearing 8.
  • the FIG. 8 shows a position of the engine after passing through the top dead center OT at a setting for large stroke.
  • the aspect ratio between the effective lever arm H4 of the connecting rod 4 on the transmission lever 5 and the effective lever arm H6 connected to the piston 2 pull and push rod 6 is about 7 to 10.
  • FIGS. 9 and 10 the engine is shown at a low lift setting.
  • the FIG. 9 shows the engine elements at a piston position at top dead center TDC and FIG. 10 at a piston position at bottom dead center UT.
  • the transmission lever 5 moved by the connecting rod 4 pivots about the angle ⁇ 5, whereby the piston 2 travels the path S.
  • FIG. 9 the engine elements are shown at a piston position at top dead center OT.
  • the aspect ratio between the effective lever arm H4 of the connecting rod 4 on the transmission lever 5 and the effective lever arm H6 of the connected to the piston 2 pull and push rod 6 is about 2 to 10.
  • the solution according to the invention is in addition to the reciprocating internal combustion engines for other reciprocating engines, such. B. for axial compressor or expander, can be used.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transmission Devices (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (9)

  1. Moteur à combustion interne à piston alternatif comprenant un mécanisme d'embiellage et un levier de transmission accouplé de manière indirecte au piston, coupant l'axe du cylindre, qui est articulé d'une part à une tige de bielle d'un mécanisme d'embiellage et d'autre part à un support sur palier guidé dans le bloc cylindre mais déplaçable,
    caractérisé par les caractéristiques suivantes :
    - le piston (2) est connecté à une barre de traction et de poussée (6),
    - la barre de traction et de poussée (6) vient en prise dans un guide (50, 51) s'étendant longitudinalement sur le levier de transmission (5),
    - un levier de guidage (9) est articulé de manière pivotante à la barre de traction et de poussée (6), et est articulé sur son côté opposé à la barre de traction et de poussée (6) de manière pivotante au bloc cylindre (ZB),
    - et le levier de transmission (5) est disposé par rapport à son articulation à la barre de traction et de poussée (6) de manière déplaçable et réglable par un entraînement de commande.
  2. Moteur à combustion interne à piston alternatif selon la revendication 1,
    caractérisé en ce que
    la barre de traction et de poussée (6) est connectée au levier de transmission (5) par le biais d'un sabot coulissant (7) pivotant, monté sur la barre de traction et de poussée (6), le sabot coulissant (7) venant en prise dans un guide (50) s'étendant le long du levier de transmission (5).
  3. Moteur à combustion interne à piston alternatif selon la revendication 1,
    caractérisé en ce que
    la barre de traction et de poussée (6) vient en prise avec un tourillon (61) dans un trou oblong (51) du levier de transmission (5).
  4. Moteur à combustion interne à piston alternatif selon les revendications 1 à 3,
    caractérisé en ce que
    le levier de guidage (9) est monté fixement mais de manière pivotante sur le bloc cylindre (ZB).
  5. Moteur à combustion interne à piston alternatif selon les revendications 1 à 4,
    caractérisé en ce que
    le support sur palier déplaçable (8) du levier de transmission (5) est disposé de manière guidée transversalement à l'axe du cylindre (ZA) dans le bloc cylindre (ZB).
  6. Moteur à combustion interne à piston alternatif selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le guidage sur palier (8ZB) est orienté transversalement à l'axe du cylindre (ZA), mais de manière inclinée.
  7. Moteur à combustion interne à piston alternatif selon les revendications 1 à 3,
    caractérisé en ce que
    le levier de guidage (9) est articulé de manière pivotante à un guide coulissant (10) déplaçable verticalement sur le bloc cylindre (ZB).
  8. Moteur à combustion interne à piston alternatif selon la revendication 7,
    caractérisé en ce que
    l'entraînement de commande pour le déplacement de l'articulation de la barre de traction et de poussée (6) au levier de transmission (5) se compose d'une roue à denture hélicoïdale (11) pouvant pivoter sur un arbre de vis sans fin entraîné (12), sur laquelle sont disposés de manière pivotante, à distance de son point de pivotement (16), un levier d'avance (14) et une bielle oscillante (15), l'autre extrémité du levier d'avance (14) étant connectée de manière pivotante au guide coulissant (10) déplaçable et au levier de guidage (9) et l'autre extrémité de la bielle oscillante (15) étant connectée de manière pivotante à une extrémité du levier de transmission (5).
  9. Moteur à combustion interne à piston alternatif selon les revendications 7 et 8,
    caractérisé en ce que
    la bielle oscillante (15) est disposée de manière à pouvoir pivoter par le biais d'un levier à deux frappes (13) disposé de manière fixe mais pivotante sur le bloc cylindre (ZB), autour de son point de pivotement (17).
EP06025534A 2006-01-24 2006-12-11 Moteur à combustion à piston élévateur Not-in-force EP1811151B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006003737A DE102006003737B3 (de) 2006-01-24 2006-01-24 Hubkolben-Verbrennungsmotor

Publications (3)

Publication Number Publication Date
EP1811151A2 EP1811151A2 (fr) 2007-07-25
EP1811151A3 EP1811151A3 (fr) 2008-07-02
EP1811151B1 true EP1811151B1 (fr) 2010-10-06

Family

ID=37964415

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06025534A Not-in-force EP1811151B1 (fr) 2006-01-24 2006-12-11 Moteur à combustion à piston élévateur

Country Status (5)

Country Link
US (1) US7455041B2 (fr)
EP (1) EP1811151B1 (fr)
KR (1) KR101332561B1 (fr)
AT (1) ATE483903T1 (fr)
DE (2) DE102006003737B3 (fr)

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Also Published As

Publication number Publication date
EP1811151A3 (fr) 2008-07-02
EP1811151A2 (fr) 2007-07-25
KR101332561B1 (ko) 2013-11-22
US20070169739A1 (en) 2007-07-26
KR20070077797A (ko) 2007-07-27
ATE483903T1 (de) 2010-10-15
DE502006008011D1 (de) 2010-11-18
DE102006003737B3 (de) 2007-06-06
US7455041B2 (en) 2008-11-25

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